Refrigeration system with modulated condensing loops

ABSTRACT

A refrigeration system having a main refrigeration circuit having a condensing stage, wherein a first refrigerant in a high pressure gas state is condensed at least partially to a liquid state. The condensing stage has a pair of  stand-alone condensing stage closed loops  in heat exchange relation with the main refrigeration circuit. The stand-alone condensing stage closed loops are  is in parallel one to another  with a condenser of the condensing stage and each comprise  comprises a second refrigerant circulating between at least a heat absorption stage, wherein the second refrigerant absorbs heat from the first refrigerant in the main refrigeration circuit so as to condense the first refrigerant to the liquid state, and a heat release stage, wherein the second refrigerant releases the absorbed heat. The condensing stage has modulating valves for selectively and quantitatively modulating the temperature of said first refrigerant and compressor head pressure.

FIELD OF THE INVENTION

The present invention generally relates to refrigeration systems, andmore particularly, to modulate closed condensing loops for usetherewith.

BACKGROUND OF THE INVENTION

In a typical refrigeration system, particularly those found insupermarkets, a plurality of evaporators are used to refrigeratefoodstuff in refrigerated display cases. Such systems basically comprisea closed circuit having a compressor stage, a condenser stage, anexpansion stage and an evaporator stage. Other stages may be added tothe above described basic refrigeration circuit in order to recuperateheat, or to provide refrigeration systems with defrosting loops for highspeed defrosting of the evaporators. For instance, U.S. Pat. No.5,673,567, issued on Oct. 7, 1997 to the present assignee, discloses arefrigeration system with a heat reclaim loop for recuperating heat fromhot high pressure refrigerant gas outletting from the compressor stage,rather than evacuating the heat through the condensers, where the heatwould be lost to the atmosphere. Thus, the heat reclaim loop is providedin parallel to the condenser stage in order to recuperate heat in heatexchange devices rather than rejecting it to the atmosphere. Preferably,in the cooler seasons, the heat is used for heating the entrance areaand other specific colder areas of supermarkets. In the warmer months,the heat may be recuperated for heating water.

U.S. Pat. No. 5,826,433, issued on Oct. 27, 1998 to the presentassignee, discloses modification to the above described patent, wherebya modulating valve is provided for efficiently controlling the rate ofheat reclaim versus the heat rejection through the condenser stage.

Finally, U.S. Pat. No. 6,089,033, issued on Jul. 18, 2000 to the presentassignee discloses a refrigeration system configuration in order todefrost evaporator units at higher speeds.

These refrigeration systems, and generally most refrigeration systemsused in supermarkets, have roof top condensers in order to reject heatat the outlet of the compressor stage, whereby the refrigerant iscondensed at least partially to a liquid state. Unfortunately, the loopsto the roof top condensers extend the piping length of the refrigerationsystem. Accordingly, the piping networks of refrigeration systems arefilled with refrigerant to provide every stage with the necessaryconditions for refrigeration. Furthermore, with the advent of heatreclaim loops and high speed defrost cycles, even more refrigerant isused.

Unfortunately, the refrigerants typically used in such refrigerationsystems (i.e. refrigerants 404, 408, 507, AZ-20 and the like) areexpensive and are often volatile, whereby they may be hazardous to humanhealth and to the environment. The more these refrigerants are used, thehigher is the risk of polluting the environment.

SUMMARY OF THE INVENTION

It is a feature of the present invention to provide a refrigerationsystems having reduced amounts of the above stated refrigerants.

It is a further feature of the present invention to provide arefrigeration system optimizing heat reclaim with respect to compressoroperation.

According to the above feature of the present invention, and from abroad aspect thereof, the present invention provides a refrigerationsystem having a main refrigeration circuit having a condensing stage,wherein a first refrigerant in a high pressure gas state is condensed atleast partially to a liquid state. The condensing stage ha a pair ofstand-alone condensing stage closed loops in heat exchange relation withthe main refrigeration circuit. The stand-alone condensing stage closedloops are parallel one to another and each comprise a second refrigerantcirculating between at least a heat absorption stage, wherein the secondrefrigerant absorbs heat from the first refrigerant in the mainrefrigeration circuit so as to condense the first refrigerant to theliquid state, and a heat release stage, wherein the second refrigerantreleases the absorbed heat. The condensing stage has modulating valvesfor selectively and quantitatively modulating the temperature of saidfirst refrigerant and compressor head pressure.

Therefore, in accordance with the present invention, there is provided arefrigeration system having a main refrigeration circuit, wherein afirst refrigerant goes through at least a compressing stage, whereinsaid first refrigerant is compressed to a high pressure gas state tothen reach a condensing stage, wherein said high pressure gasrefrigerant is condensed at least partially to a liquid state to thenreach an expansion stage, wherein said high pressure liquid refrigerantis expanded to a low pressure liquid state to then reach an evaporatorstage, wherein said low pressure liquid refrigerant is evaporated atleast partially to a low pressure gas state by absorbing heat, to thenreturn to said compressing stage, said condensing stage having at leastone stand-alone condensing stage closed loop in heat exchange relationwith said main refrigeration circuit, said stand-alone condensing stageclosed loop being in parallel with a condenser of the condensing stageand comprising a second refrigerant circulating between at least a heatabsorption stage, wherein said second refrigerant absorbs heat from aportion of said first refrigerant in said main refrigeration circuit soas to condense said first refrigerant to said liquid state, and a heatrelease stage, wherein said second refrigerant releases said absorbedheat, said condensing stage having modulating valve means forselectively and quantitatively modulating the temperature of said firstrefrigerant and compressor head pressure.

Further in accordance with the present invention, there is provided arefrigeration system having a main refrigeration circuit, wherein afirst refrigerant goes through at least a compressing stage, whereinsaid first refrigerant is compressed to a high pressure gas state tothen reach a condensing stage, wherein said high pressure gasrefrigerant is condensed at least partially to a liquid state to thenreach an expansion stage, wherein said high pressure liquid refrigerantis expanded to a low pressure liquid state to then reach an evaporatorstage, wherein said low pressure liquid refrigerant is evaporated atleast partially to a low pressure gas state by absorbing heat, to thenreturn to said compressing stage, said condensing stage having at leasta pair of stand-alone condensing stage closed loops in heat exchangerelation with said main refrigeration circuit, said stand-alonecondensing stage closed loops being parallel one to another and eachcomprising a second refrigerant circulating between at least a heatabsorption stage, wherein said second refrigerant absorbs heat from saidfirst refrigerant in said main refrigeration circuit so as to condensesaid first refrigerant to said liquid state, and a heat release stage,wherein said second refrigerant releases said absorbed heat, saidcondensing stage having modulating valve means for selectively andquantitatively modulating the temperature of said first refrigerant andcompressor head pressure as a function of at least one of an outdoortemperature and an indoor ambient temperature.

BRIEF DESCRIPTION OF THE DRAWINGS

A preferred embodiment of the present invention will now be described indetail having reference to the accompanying drawings in which:

FIG. 1 is a schematic diagram illustrating a stand-alone evaporativecondenser loop of the present invention;

FIG. 2 is a schematic diagram depicting a stand-alone heat reclaim loopof the present invention; and

FIG. 3 is a schematic diagram illustrating a refrigeration system havingthe stand-alone evaporative condenser loop and heat reclaim loop.

DESCRIPTION OF PREFERRED EMBODIMENTS

Referring to FIG. 1, there is generally shown at 10 a stand-aloneevaporative condenser loop of the present invention. The loop 10comprises a plate heat exchanger 12 for the heat exchange between arefrigerant A in a refrigeration system and a refrigerant B in theevaporative condenser loop 10. Refrigerant A of the refrigeration systementering the heat exchanger 12 is from the output of compressors in ahigh pressure hot gas state, and goes through the heat exchanger 12 torelease latent heat by condensing, to then exit therefrom at leastpartially in a high pressure liquid state. Thus, a gas refrigerant linefrom the refrigeration system is shown entering the heat exchanger 12through inlet line 1, whereas a liquid refrigerant line exits the heatexchanger 12 at outlet line O. The refrigeration system will bedescribed in further detail hereinafter.

The condensing loop 10 has an evaporative condenser 14. The evaporativecondenser 14 typically comprises a coiling system therein, across whicha fluid flows in order for refrigerant within the coiling system torelease heat it has previously absorbed in the heat exchanger 12. Forinstance, the fluid may be air or a spray of water flowing over thecoiling system. A condenser feedline 16 connects the heat exchanger 12to the evaporative condenser 14. It is pointed out that the condensingloop 10 may be provided with a plurality of evaporative condensers 14,wherefore a branch line 18 is shown diverging from the condenserfeedline 16 to add similar evaporative condensers 14 in parallel to thefirst one. The condenser feedline 16 is provided with valves and controldevices to ensure the flow direction and the proper refrigerantconditions. For instance, a manometer 20 is shown mounted in thecondenser feedline 16, as well as a plurality of check valves 22.

A condenser return line is generally shown at 24 and connects theevaporative condenser 14 to the heat exchanger 12, so as ensure the flowof cooled refrigerant from the evaporative condenser 14 to the heatexchanger 12. A pump 26 is provided in the condenser return line 24 toensure the flow of the refrigerant B in the condensing loop 10. A filter28 in the condenser return line 24 filters out the refrigerant. Furthercheck valves 22 and manometer 20 are provided in the condenser returnline 24. Furthermore, parallel loops (not shown) along with manuallyoperated valves (e.g. three-way valves, ball valves, butterfly valves)may also be provided in order to isolate the various components of thecondensing loop 10 for maintenance or for servicing purposes. A branchline 30 is shown connecting to the condenser return line 24 in the eventwhere more than one evaporative condenser 14 are part of the condensingloop 10.

Referring now to FIG. 2, a stand-alone heat reclaim loop in accordancewith the present invention is generally shown at 50. The heat reclaimloop 50 comprises a plate heat exchanger 52, provided for absorbing heatfrom a refrigerant A in a refrigeration system. The refrigerant A in therefrigeration system is in a high pressure hot gas state when enteringthe heat exchanger 52 and is condensed to a liquid state to then exitthe heat exchanger 52. The inlet line of hot pressure gas refrigerant Ais shown at 12, whereas the outlet of condensed liquid refrigerant A isshown at outlet line O2.

The heat reclaim loop 50 has a heat reclaim coil 54 and a air heatingunit 56. The heat reclaim coil 54 is typically installed in aventilation duct through which air circulates, so as to warm up the air.The air heating unit 56 is typically provided for heating areas whereventilation is not required (e.g. shipping dock, entrance). It ispointed out that the heat reclaim loop 50 may be limited to either oneof the heat reclaim coil 54 and the heating unit 56, or may even have aplurality of both. A heat reclaim feedline 58 connects the heatexchanger 52 to the heat reclaim coil 54 and to the air heating unit 56to ensure the flow of a refrigerant B therebetween. An accumulation tank60 is connected in the heat reclaim feedline 58 for accumulatingrefrigerant B having absorbed heat in the heat exchanger 52. A pump 62is also mounted in the heat reclaim feedline 58, downstream from theaccumulation tank 60 to ensure the flow of refrigerant B from theaccumulation tank 60 to the heat reclaim coil 54 and the air heatingunit 56. A heat reclaim return line 64 connects the heat reclaim coil 54and the air heating unit 56 to the heat exchanger 52, thereby ensuringthe flow of refrigerant B from the formers to the latter.

The heat reclaim coil 54 has an inlet line 66 separated from the heatreclaim feedline 58 by a three-way valve 68. A by-pass line 70 isconnected to the free port of the three-way valve 68 and converges withan outlet line 72 of the heat reclaim coil 54 to reach the heat reclaimreturn line 64. Thus, the three-way valve 68 controls the flow ofrefrigerant B from the heat reclaim feedline 58 to the heat reclaim coil54. The three-way valve 68 may be fully closed to the inlet line 66 ofthe heat reclaim coil 54, whereby refrigerant B flows through theby-pass line 70 to reach the heat reclaim return line 64. It is pointedout that the outlet line 72 comprises a check valve 74 such thatrefrigerant by-passing the heat reclaim coil 54 is prevented fromentering same through the outlet line 72 thereof.

The air heating unit 56 is connected to the heat reclaim loop 50 inparallel to the heat reclaim coil 54. The heating unit 56 has an inletline 76 connected to the heat reclaim feedline 58 through a three-wayvalve 78. The free port of the three-way valve 78 is connected to aby-pass line 80 which converges with an outlet line 82 of the heatingunit 56 to connect to the heat reclaim return line 64. Similarly to theheat reclaim coil 54, the flow of refrigerant B to the heating unit 56is controlled by the three-way valve 78. Once more, the heating unit 56may be by-passed by the refrigerant B, whereby refrigerant B circulatesthrough the by-pass line 80 and is prevented from entering the heatingunit 56 by the check valve 84 mounted therein.

The pump 62 and the accumulation tank 60 allow storage of refrigerant B,having absorbed heat in the heat exchanger 52. If the heat reclaim coil54 and the air heating unit 56 are in standby (by being by-passed) asthe demand for heating air is low, the tank 60 accumulates the heatedrefrigerant B such that the heat reclaim loop 50 is able to sustainsudden and rapid increases in demand of heating air. The pump 62 maystop operating beyond certain levels of refrigerant B. It is pointed outthat the accumulation tank 60 may be insulated to keep the refrigeranttherein in given states. The pump 62 may be automated in order tooperate automatically according to factors such as outdoor and indoortemperatures, as well as refrigerant B temperature. Increasedrefrigerant B demand may thus be anticipated and fulfilled by the pump62 and the accumulation tank 60.

The heat reclaim loop 50 comprises various devices for the control ofthe refrigerant parameters, such as the direction of flow, the pressureand the filtering. For instance, filter 86, check valves 88 andmanometers 90 are provided in the heat reclaim loop 50 for the abovedescribed reasons.

Now that both the stand-alone evaporative condenser loop 10 and heatreclaim loop 50 have been described in detail, a typical refrigerationsystem in which the formers may be used will now be described. Becausethe stand-alone condensing loops use non-polluting refrigerants such asglycol, there is a reduction in the quantity of refrigerant required inthe conventional portion of the refrigeration system.

Referring now to FIG. 3, a refrigeration system 100 is typically adaptedfor receiving the stand-alone evaporative condenser loop 10 described inFIG. 1 and the heat reclaim loop 50 described in FIG. 2. The evaporativeloop 10 and the heat reclaim loop 50 are shown connected to therefrigeration system 100 parallel one to another. Similarly to thedescription of the loops 10 and 50, for clarity purposes, a refrigerant,identified as refrigerant A, which will be discussed hereinafter, flowsin the refrigeration system 100, whereas a refrigerant, referred to asrefrigerant B, flows in the loops 10 and 50. Furthermore, as theinvention resides in the portion of the refrigeration system involvingthe stand-alone evaporative condenser loop 10 and the stand-alone heatreclaim loop 50, which have been described extensively above, therefrigeration system 100 will only be described schematically. Forinstance, the refrigeration system 100 shown in FIG. 3 comprises highspeed defrost loops which will not be described herein.

As shown in FIG. 3, the refrigeration system 100 comprises a pluralityof compressors 102. Refrigerant A from compressors 102 is in a highpressure gas state. A header 106 and a high pressure gas line 108 areconnected to the outlets of the compressors 102 so as to convey the highpressure gas refrigerant A exiting therefrom to a three-way controlvalve 104 and modulating valves 105 and 107, which separates the highpressure gas line 108 into an evaporative condenser line 110 and a heatreclaim line 112. Both the evaporative condenser line 110 and the heatreclaim line 112 will converge to a liquid refrigerant reservoir 114,after having high pressure gas refrigerant A gone through heatexchangers 12 and 52 of the evaporator condenser loop 10 and the heatreclaim loop 50, respectively. Therefore, as the evaporative condenserline 110 and the heat reclaim line 112 diverge at the valves 104, 105and 107 and converge at the refrigeration reservoir 114, these lines areparallel one to another. It is pointed out that the evaporativecondenser line 112 was referred to as input line I and output line O inFIG. 1, wherefore reference letters I and O have been added to FIG. 3.Similarly, the heat reclaim line 112 was referred to in FIG. 2 as inletline 12 and outlet line O2, wherefore reference letters for the lattershave been added to FIG. 3.

The three-way control valve 104 and the modulating valves 105 and 107are adapted to control the amounts of refrigerant A flowing to theevaporative condenser line 110 and the heat reclaim line 112. A mainobjective of the refrigeration system 100 is to recuperate as much heatas possible from the refrigerant A requiring to be condensed at leastpartially to a liquid state. However, in order to keep the operationcosts low for such a refrigeration system, the compressor 102 mustoperate with the head pressures as low as possible, yet by fulfillingthe compression needs of the system. By the use of parallel condenserline 110 and heat reclaim line 112, it is possible to optimize the headpressure of the refrigerant A in the main refrigeration system 100.According to a plurality of factors which will be described hereinafter,the three-way control valve 104 and the modulating valves 105 and 207can completely shut the feeding of high pressure gas refrigerant A toeither one of the heat exchanger 12 and heat exchanger 52, as well asmodulate and control the output pressure of the compressor 102. Asmentioned in the description of the evaporative condenser loop 10 andthe heat reclaim loop 50, the high pressure gas refrigerant A exitingthe heat exchangers 12 and 52, respectively, through outlet lines O andO2, is in a high pressure liquid state.

Typically, the head pressure in the condenser line 110 floats in orderto maintain the pressure of refrigerant A in this portion of therefrigeration system at a relatively low pressure. As the evaporativecondenser loop 10 has great cooling capacities due to the use of waterto cool refrigerant B, which then cools refrigerant A through heatexchanger 12, the condenser line 110 allows lowering of the outputrefrigerant A pressure of the compressors 102, thereby resulting inenergy savings. Modulating valves 105 and 107 modulate the outputpressure of the compressors 102. One, for instance, may operate at lowerpressures, whereas the other works at higher pressures. The pressure ofrefrigerant A varies according to a few factors. The compressors mustoperate as little as possible, as they increasingly consume electricityas a function of their pressure output. On the other hand, therefrigerant released from the compressors 102 must be at a temperatureabove that of the cooling fluid, usually a predetermined constantpressure differential (e.g., +15° C.). In the present invention, thecooling fluid is refrigerant B, which is actually cooled by theventilation air in the heat reclaim coil 54 or the heating unit 56 inthe case of the heat reclaim line 112, and by water in the evaporativecondenser 14 in the case of the evaporative condenser line 10.Therefore, the temperature and pressure of the refrigerant A aremodulated in accordance with the heat reclaim demand, the indoor airtemperature and the outdoor air temperature.

Thereafter, high pressure liquid refrigerant A accumulated in the liquidrefrigerant reservoir 114 flows through a liquid refrigerant line 116and liquid refrigerant header 118 to reach the expansion valves 120 ofthe refrigeration system 100. High pressure liquid refrigerant A flowingacross the expansion valves 120 expands to be lowered in pressure.Therefore, refrigerant A, in a low pressure liquid state, flows toevaporators 122 through evaporator inlet lines 124, which extend betweenthe expansion valves 120 and the evaporators 122. The low pressureliquid A is at a temperature well below the desired temperature of therefrigerator units (not shown). The refrigerant A absorbs heat in theevaporators 122, whereby it exits the evaporators 122 in a gas state.The low pressure liquid refrigerant A exists the evaporators 122 inevaporator outlet lines 126 to reach a suction header 128 to then returnto the compressors 102.

Typical refrigerants used as refrigerant A are refrigerants 404, 408,507, AZ-20. The typical refrigerants used as refrigerant A may bevolatile, whereby they are a threat to the environment as they evaporateat ambient conditions. Furthermore, they are toxic and are likelyhazardous to health. The evaporative condenser loop 10 and the heatreclaim loop 50 allow for the reduction of size of the refrigerationsystem 100. Typically, the evaporative condenser line 110 and the heatreclaim line 112 extend from the compressors 102 to the roof top of thebuilding to reach condensers of the condenser stage, wherein heat isreleased to the environment. Accordingly, these lengthy networks ofpiping must be filled with refrigerant A for the proper functioningthereof.

The stand-alone evaporative condenser loop 10 and heat reclaim loop 50extend from adjacent the compressors 102 to the various condensing unitsthereof, namely the evaporative condenser 14, the heat reclaim coil 54and the air heating unit 56. Therefore, the evaporative condenser line110 and the heat reclaim line 112 are substantially shortened, wherebythe amount of refrigerant A in the refrigeration system 100 is greatlyreduced. As the refrigerant B must not sustain great variations intemperature as compared to the refrigerant A which must rise above theoutdoor temperature to condense and drop below the refrigeratortemperature to evaporate, the sole purpose of the refrigerant B is toabsorb heat to condense the refrigerant A. Therefore, refrigerant B maybe any of the following: ethylic acetate, acetic acid, sulfuric acid,ammoniac, calcium chloride, hydrogen chloride, methylene chloride,sodium chloride, vinyl chloride, carbon dioxide, ethanol, ethyleneglycol, acetate formiate, potassium formiate, iso-butane, Pekasol 50,propane, propylene glycol, toluene, trichloroethylene. In any event,refrigerant B is chosen amongst safer fluids than refrigerant A. As thepiping of the refrigeration system 100 is greatly reduced, thecompressors 102 are not required to outlet compressed refrigerant atpressures as high as for longer refrigeration lines. The compressors canoperate at head pressures of about 120 psi instead of 220 psi, therebyreducing their operating time and increasing their life-span. Therefore,substantial savings are achieved in electricity consumption of thecompressors 102, and the life of the compressors 102 is increased.

The three-way control valve 104 and the modulating valves 105 and 107redirect the flow of refrigerant A towards heat exchanger 12 or heatexchanger 52 according to the seasonal heat requirements of the buildingin which the refrigeration system 100 is. The stand-alone heat reclaimloop 50 advantageously recuperates the heat produced by the compressors102. The evaporative condenser 14 of the stand-alone evaporativecondenser loop 10 may either release the heat outdoors, or recover theheat by, for instance, spraying a liquid such as water on the coils ofthe evaporative condenser 14 to absorb the excess heat. Thus, in thefall, winter and spring seasons, a greater amount of refrigerant iscirculated in the heat exchanger 52, whereby the heat absorbed fromrefrigerant A will serve for heating the building. It is pointed outthat the refrigeration system 100 may be provided with only one of theevaporative condenser loop 10 or the heat reclaim loop 50.

It is within the ambit of the present invention to cover any obviousmodifications of the embodiments described herein, provided suchmodifications fall within the scope of the appended claims.

What is claimed is:
 1. A refrigeration system having a mainrefrigeration circuit, wherein a first refrigerant goes through at leasta compressing stage, wherein said first refrigerant is compressed to ahigh pressure gas state to then reach a condensing stage, wherein saidhigh pressure gas refrigerant is condensed at least partially to aliquid state to then reach an expansion stage, wherein said highpressure liquid refrigerant is expanded to a low pressure liquid stateto then reach an evaporator stage, wherein said low pressure liquidrefrigerant is evaporated at least partially to a low pressure gas stateby absorbing heat, to then return to said compressing stage, saidcondensing stage having at least a pair of one stand-alone condensingstage closed loops in heat exchange relation with said mainrefrigeration circuit, said stand-alone condensing stage closed loopsbeing in parallel one to another with a condenser of a condensing stageand each comprising a second refrigerant circulating between at least aheat absorption stage, wherein said second refrigerant absorbs heat froma portion of said first refrigerant in said main refrigeration circuitso as to condense said first refrigerant to said liquid state, and aheat release stage, wherein said second refrigerant releases saidabsorbed heat, said condensing stage having modulating valve means forselectively and quantitatively modulating the temperature of said firstrefrigerant and compressor head pressure.
 2. The refrigeration systemaccording to claim 1, wherein said second refrigerant is one of ethylicacetate, acetic acid, sulfuric acid, ammoniac, calcium chloride,hydrogen chloride, methylene chloride, sodium chloride, vinyl chloride,carbon dioxide, ethanol, ethylene glycol, acetate formiate, potassiumformiate, iso-butane, Pekasol 50, propane, propylene glycol, toluene,and trichloroethylene.
 3. The refrigeration system according to claim 1,wherein said heat exchange relation between said main refrigerationcircuit and said condensing stage closed loops is achieved by plate heatexchangers.
 4. The refrigeration system according to claim 1, whereinsaid heat release stage of a first of said closed loops comprises atleast one of a heat reclaim coil and a heating unit, and a second one ofsaid closed loops comprises an evaporative condenser .
 5. Therefrigeration system according to claim 4, wherein said heat releasestage of said first of said closed loops comprises valves to selectivelychose flow of said second refrigerant through at least one of said heatreclaim coil and said heating unit.
 6. The refrigeration systemaccording to claim 1, wherein absorbed heat from said second refrigerantin said heat release stage is released by at least one of beingevacuated outdoors, heating water and heating air.
 7. The refrigerationsystem according to claim 6, further comprising valves for selecting thereleasing of said absorbed heat from said second refrigerant in saidheat release stage.
 8. The refrigeration system according to claim 1,further comprising an absorbed heat reservoir downstream from said heatabsorption stage in said first of said closed loops , wherein saidsecond refrigerant is accumulated prior to being fed to said heatrelease stage.
 9. The refrigeration system according to claim 1, whereinsaid modulating valve means comprises at least a valve for selectivelyand quantitatively directing flow of said first refrigerant for heatexchanging with said closed loops .
 10. The refrigeration systemaccording to claim 9, wherein said modulating valve means comprises twomodulating valves and a three-way directional valve connecting saidcompressing stage to said condensing stage.
 11. A refrigeration systemhaving a main refrigeration circuit, wherein a first refrigerant goesthrough at least a compressing stage, wherein said first refrigerant iscompressed to a high pressure gas state to then reach a condensingstage, wherein said high pressure gas refrigerant is condensed at leastpartially to a liquid state to then reach an expansion stage, whereinsaid high pressure liquid refrigerant is expanded to a low pressureliquid state to then reach an evaporator stage, wherein said lowpressure liquid refrigerant is evaporated at least partially to a lowpressure gas state by absorbing heat, to then return to said compressingstage, said condensing stage having at least a pair of stand-alonecondensing stage closed loops in heat exchange relation with said mainrefrigeration circuit, said stand-alone condensing stage closed loopsbeing parallel one to another and each comprising a second refrigerantcirculating between at least a heat absorption stage, wherein saidsecond refrigerant absorbs heat from said first refrigerant in said mainrefrigeration circuit so as to condense said first refrigerant to saidliquid state, and a heat release stage, wherein said second refrigerantreleases said absorbed heat, said condensing stage having modulatingvalve means for selectively and quantitatively modulating thetemperature of said first refrigerant and compressor head pressure as afunction of at least one of an outdoor temperature and an indoor ambienttemperature.
 12. The refrigeration system according to claim 11, whereinsaid second refrigerant is one of ethylic acetate, acetic acid, sulfuricacid, ammoniac, calcium chloride, hydrogen chloride, methylene chloride,sodium chloride, vinyl chloride, carbon dioxide, ethanol, ethyleneglycol, acetate formiate, potassium formiate, iso-butane, Pekasol 50,propane, propylene glycol, toluene, and trichloroethylene.
 13. Therefrigeration system according to claim 11, wherein said heat exchangerelation between said main refrigeration circuit and said condensingstage closed loops is achieved by plate heat exchangers.
 14. Therefrigeration system according to claim 11, wherein said heat releasestage of a first of said closed loops comprises at least one of a heatreclaim coil and a heating unit, and a second one of said closed loopscomprises an evaporative condenser.
 15. The refrigeration systemaccording to claim 14, wherein said heat release stage of said first ofsaid closed loops comprises valves to selectively chose flow of saidsecond refrigerant through at least one of said heat reclaim coil andsaid heating unit.
 16. The refrigeration system according to claim 11,wherein absorbed heat from said second refrigerant in said heat releasestage is released by at least one of being evacuated outdoors, heatingwater and heating air.
 17. The refrigeration system according to claim16, further comprising valves for selecting the releasing of saidabsorbed heat from said second refrigerant in said heat release stage.18. The refrigeration system according to claim 11, further comprisingan absorbed heat reservoir downstream from said heat absorption stage insaid first of said closed loops, wherein said second refrigerant isaccumulated prior to being fed to said heat release stage.
 19. Therefrigeration system according to claim 11, wherein said modulatingvalve means comprises at least a valve for selectively andquantitatively directing flow of said first refrigerant for heatexchanging with said closed loops.
 20. The refrigeration systemaccording to claim 19, wherein said modulating valve means comprises twomodulating valves and a three-way directional valve connecting saidcompressing stage to said condensing stage.
 21. The refrigeration systemaccording to claim 1, wherein the condenser of the condensing stage isin a second stand-alone condensing stage closed loop in heat exchangerelation with said main refrigeration circuit, said second closed loopalso comprising said second refrigerant circulating between at least aheat absorption stage, wherein said second refrigerant absorbs heat froma portion of said first refrigerant in said main refrigeration circuitso as to condense said first refrigerant to said liquid state, and aheat release stage, wherein said second refrigerant releases saidabsorbed heat.
 22. The refrigeration system according to claim 21,wherein the condenser is an evaporation condenser.